Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
  • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
  • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
  • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
  • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
  • F15B15/20—Other details, e.g. assembly with regulating devices
  • F15B15/204—Control means for piston speed or actuating force without external control, e.g. control valve inside the piston
• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
  • E02F9/20—Drives; Control devices
  • E02F9/22—Hydraulic or pneumatic drives
  • E02F9/2221—Control of flow rate; Load sensing arrangements
  • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
  • E02F9/2228—Control of flow rate; Load sensing arrangements using pressure-compensating valves including an electronic controller
• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
  • E02F9/20—Drives; Control devices
  • E02F9/22—Hydraulic or pneumatic drives
  • E02F9/2278—Hydraulic circuits
  • E02F9/2285—Pilot-operated systems
• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
  • E02F9/26—Indicating devices
  • E02F9/264—Sensors and their calibration for indicating the position of the work tool
  • E02F9/265—Sensors and their calibration for indicating the position of the work tool with follow-up actions (e.g. control signals sent to actuate the work tool)
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
  • F15B21/12—Fluid oscillators or pulse generators
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B2211/00—Circuits for servomotor systems
  • F15B2211/30—Directional control
  • F15B2211/32—Directional control characterised by the type of actuation
  • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
  • F15B2211/328—Directional control characterised by the type of actuation electrically or electronically with signal modulation, e.g. pulse width modulation [PWM]
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B2211/00—Circuits for servomotor systems
  • F15B2211/30—Directional control
  • F15B2211/32—Directional control characterised by the type of actuation
  • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B2211/00—Circuits for servomotor systems
  • F15B2211/30—Directional control
  • F15B2211/355—Pilot pressure control
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B2211/00—Circuits for servomotor systems
  • F15B2211/50—Pressure control
  • F15B2211/505—Pressure control characterised by the type of pressure control means
  • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B2211/00—Circuits for servomotor systems
  • F15B2211/80—Other types of control related to particular problems or conditions
  • F15B2211/86—Control during or prevention of abnormal conditions
  • F15B2211/863—Control during or prevention of abnormal conditions the abnormal condition being a hydraulic or pneumatic failure
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B2211/00—Circuits for servomotor systems
  • F15B2211/80—Other types of control related to particular problems or conditions
  • F15B2211/86—Control during or prevention of abnormal conditions
  • F15B2211/8646—Control during or prevention of abnormal conditions the abnormal condition being hysteresis

Definitions

• a typical excavator implement includes a hydraulically driven boom, stick, and bucket members each with a respective hydraulic cylinder and can be moved by applying hydraulic fluid pressure to the cylinder.
• Various valves are used to apply the hydraulic fluid pressure to the cylinders based on input from a user.
• One problem associated with these valves is that they can cause a delay between user input and movement of an implement. This delay is caused, at least in part, by static friction, which prevents immediate movement of a valve component in response to hydraulic fluid pressure urging the component to move. Static friction is the friction occurring between two surfaces that resists movement of the surfaces relative to each other. As hydraulic fluid pressure urging the component to move increases, static friction is overcome and only kinetic friction remains, which requires less force than static friction to overcome. For example, in a pilot style system in which pilot valves actuate in response to user input, a pilot valve applies increasing hydraulic fluid pressure urging a hydraulic component to actuate, static friction is overcome and only kinetic friction remains. These static friction delays can make control of movement of the members of an implement by a user more complex and confusing.
• a method for mitigating static friction includes the steps of dithering a first hydraulic valve (i.e., continuous back and forth motion of the valve) and dithering a second hydraulic valve. Outputs of each of the first hydraulic valve and the second hydraulic valve are connected to inputs of a main hydraulic valve. The main hydraulic valve dithers in response to hydraulic fluid pressure applied to its inputs that occur due to dithering of the first hydraulic valve and the second hydraulic valve. User input is received to actuate a hydraulic cylinder associated with the main valve.
• a controller transmits a signal to the first hydraulic valve which causes hydraulic fluid pressure to be applied to one of the inputs of the main valve in response to the user input.
• the hydraulic cylinder associated with the main valve is actuated by the application of hydraulic fluid pressure from one of the outputs of the main valve in response to the hydraulic fluid pressure applied to a corresponding input of the main valve.
• FIG. 1 A depicts a simplified main hydraulic valve
• FIG. 1 B depicts a construction machine, specifically an excavator, for modifying a construction site
• FIG. 2 depicts an electronic control system associated with the excavator
• FIG. 3 depicts a schematic of a portion of a hydraulic system of the excavator;
• FIG. 4 depicts a graph of a signal applied to a controller boom-up valve from a controller;
• FIG. 5 depicts a graph of a signal applied to a user boom-up valve from the controller
• FIG. 6 depicts a graph of hydraulic fluid pressure output from a boom-up valve
• FIG. 7 depicts a graph of hydraulic fluid pressure at a first input of a main valve
• FIG. 8 depicts a graph of hydraulic fluid pressure at a second input of the main valve
• FIG. 9 depicts a graph of hydraulic fluid pressures at a first and second output of the main valve;
• FIG. 10 depicts a graph of hydraulic fluid pressure at a first input of a main valve;
• FIG. 11 depicts a graph of hydraulic fluid pressure at a second input of a main valve;
• FIG. 12 depicts a graph of hydraulic fluid pressures at a first output and a second output of the main valve.
• FIG. 13 depicts a flowchart of a method according to an embodiment of the invention.
• Stiction is the general inability of a hydraulic valve or cylinder to respond immediately and fully to a command (e.g., electrical signal or hydraulic fluid pressure) transmitted to it when it is not currently in motion.
• a command e.g., electrical signal or hydraulic fluid pressure
• an electro mechanical hydraulic valve that is not receiving a command remains at rest in a particular position.
• the valve while at rest experiences static friction which is higher than kinetic friction. Since the static friction is much higher than the kinetic friction, more force is required to begin actuation of the hydraulic valve when it is at rest than when the valve is moving.
• Stiction causes a delay from a time when an input is received to when a respective hydraulic cylinder actuated by hydraulic valves moves. Such delays can result in difficulty in controlling movement of a component driven by a hydraulic cylinder as used in various machines, such as construction machines.
• FIG 1A depicts hydraulic valve 10 having two inputs 14, 16 for receiving hydraulic fluid pressure and one output 18 for applying hydraulic fluid pressure.
• Flydraulic valve 10 has a slider 12 located within valve body 20.
• Slider 12 is a cylindrical object sized to fit within the associated cylindrical cavity of valve body 20 as shown in Figure 1 A
• Hydraulic valve 10 operates as follows. Hydraulic fluid pressure applied to input 14 urges slider away from input 14 toward input 16, compressing spring 26. Hydraulic fluid pressure applied to input 16 urges slider 12 away from input 16 toward input 14, compressing spring 28. If the hydraulic fluid pressures applied to input 14 and input 16 are substantially the same, slider 12 remains stationary.
• slider 12 will be urged to move away from the input having the higher hydraulic fluid pressure. Sufficient movement of slider 12 uncovers output 18 which allows hydraulic fluid pressure to be applied from either input 14 or input 16, depending on which input has a higher hydraulic fluid pressure applied.
• Slider 12 does not move in response to increased hydraulic fluid pressure because of static friction between slider 12 and the inner surface of valve body 20.
• slider 12 begins to move and kinetic friction, which is lower than the static friction, occurs between slider 12 and inner surface of valve body 20.
• the static friction can cause a delay between when actuation of hydraulic valve 10 is requested and when hydraulic valve 10 is actuated.
• slider 12 is sized to fit within inner surface of valve body 20 to prevent the flow of hydraulic fluid between slider 12 and valve body 20.
• O-rings are used but stiction still occurs between slider 12 and valve body 20, and in many cases the resulting stiction is higher than without O-rings.
• FIG. 1 B shows a construction machine, specifically excavator 100.
• Excavator 100 has a boom 102, a stick 104, and a bucket 106 each of which can be controlled by a user located in cab 108 of excavator 100.
• Boom 102, stick, 104, and bucket 106 together are referred to as an implement (e.g., a surface modifying implement) of excavator 100.
• Cab 108 is part of what is referred to as the body of excavator 100 which can include treads or other means of conveyance.
• the user actuates a control device (e.g., a joystick) located in cab 108 to move boom 102, ultimately via hydraulic fluid pressure applied to hydraulic cylinder 110.
• the user actuates another control device to move stick 104 via hydraulic fluid pressure applied to hydraulic cylinder 112.
• the user actuates an additional control device to move bucket 106 via hydraulic fluid pressure applied to hydraulic cylinder 116.
• a control device e.g.
• FIG. 2 depicts a schematic of components of excavator 100 related to control of boom 102 according to an embodiment.
• Controller 202 can be an electric control device such as a programmable logic controller, application specific integrated circuit (ASIC), field programmable gate array (FPGA), etc.
• controller 202 is implemented using a computer.
• Controller 202 contains a processor 218 which controls the overall operation of the controller 202 by executing computer program instructions which define such operation.
• the computer program instructions may be stored in a storage device 222, or other computer readable medium (e.g., magnetic disk, CD ROM, etc.), and loaded into memory 220 when execution of the computer program instructions is desired.
• the method steps of Figure 13 can be defined by the computer program instructions stored in the memory 220 and/or storage 222 and controlled by the processor 218 executing the computer program instructions.
• the computer program instructions can be implemented as computer executable code programmed by one skilled in the art to perform an algorithm defined by the method steps of Figure 13.
• the processor 218 executes an algorithm defined by the method steps of Figure 13.
• controller 202 is a high level representation of some of the components of such a controller for illustrative purposes.
• Sensors 204 represents one or more sensors for detecting a state of excavator 100, such as an orientation of the implement and operating parameters such as fluid pressures and temperatures.
• the orientation of the implement is determined using linear or rotary sensors and/or inertial measurement units for determining the position boom 102, stick 104, and bucket 106 of the implement.
• Inputs 208, 212 and 216 represent various input devices for operating excavator 100.
• input 208 can include one or more control devices (e.g. joysticks) for moving boom 102, stick 104, and bucket 106.
• a boom joystick can be actuated by the user to command boom 102 to raise or lower.
• a stick joystick i.e. , a joystick for controlling movement of stick 104
• a bucket joystick can be actuated by the user to command bucket 106 to move toward body of excavator 100 or away from body of excavator 100.
• inputs associated with joysticks are signals from sensors associated with each respective joystick.
• Input 208 can also include inputs from a user via input devices such as touch screens, buttons, and other types of inputs.
• Display 206 in one embodiment, is located in the cab of excavator 100 and displays information to a user.
• Display 206 can be any type of display such as a touch screen, a light emitting diode display, a liquid crystal display, etc.
• Display 206 presents various information to a user concerning a related machine, a current site plan, a desired site plan, etc.
• Controller 202 is connected to multiple electro-mechanical control valves (e.g. 210, 214, and others not shown) each associated with movement of boom 102 of excavator 100.
• An electro-mechanical control valve 210 receives electric signals from controller 202 and, in response, applies hydraulic fluid pressure to its output.
• Controller boom-up valve 210 in one embodiment, is used to control upward movement of boom 102 of excavator 100 by directing hydraulic fluid pressure to a first input of hydraulic main valve 10 that controls cylinder 110 associated with boom 102.
• Controller boom-down valve 214 is an electro-mechanical control valve that is used to control downward movement of boom 102 of excavator 100 by directing hydraulic fluid pressure to a second input of hydraulic main valve 10 connected to hydraulic cylinder 110 associated with boom 102.
• Controller 202 would typically also be connected to electric joystick control valves, via input 208 (not shown) for controlling stick 104 and bucket 106 or other machinery associated with excavator 100.
• the electro-mechanical control valves for controlling stick 104 and bucket 106 operate in a manner similar to the electro-mechanical control valves for controlling boom and are therefore not shown.
• controller 202 receives data from input 208 and sensors 204. Controller 202 analyzes the received data and determines excavator operation information for display to a user via display 206 and determines if outputs should be sent to controller boom-up valve 210 and/or controller boom-down valve 214 to control boom 102. In one embodiment, controller 202 outputs signals to controller boom-up valve 210, and/or controller boom-down valve 214, in the absence of control inputs from a user to mitigate stiction as described below.
• FIG 3 shows a schematic of a portion of a hydraulic system 300 of excavator 100 for controlling movement of boom (102 of Figure 1 ). Flydraulic systems of excavator 100 for controlling movement of stick (104 of Figure 1 ) and bucket (106 of Figure 1 ) are similar and therefore not shown.
• Hydraulic cylinder 110 is connected to boom 102 which it moves in response to hydraulic fluid pressure applied from main valve 304.
• Main valve 304 is a hydraulic valve that applies hydraulic fluid pressure to hydraulic cylinder 110 via output 332 or output 334 in response to hydraulic fluid pressure applied to input 328 or input 330 of main valve 304.
• main valve 304 when hydraulic fluid pressure is applied to input 328 and no hydraulic fluid pressure is applied to input 330, main valve 304 outputs hydraulic fluid pressure to output 332 which is applied to hydraulic cylinder 110 causing it to actuate and move boom (102 of Figure 1 B) upward.
• main valve 304 When hydraulic fluid pressure is applied to input 330 and no hydraulic fluid pressure is applied to input 328, main valve 304 outputs hydraulic fluid pressure to output 334 which is applied to hydraulic cylinder 110 causing it to actuate and move boom (102 of Figure 1 B) downward.
• Input 328 receives hydraulic fluid pressure from controller boom-up valve 210 which receives signals from controller 202, in response to user boom-up input 212 or from internally generated signals.
• Input 330 receives hydraulic fluid pressure from controller boom-down valve 214 which receives signals from controller 202, which receives signals from controller 202 based on user input received via user boom-down input 216, or from internally generated signals.
• Main valve 304 experiences stiction which can cause a delay from the time a valve is actuated by controller 202 to the time when hydraulic cylinder 110 begins to move. In one embodiment, the stiction of main valve 304 is mitigated by dithering main valve 304 via its inputs 328 and 330.
• Figures 4-12 depict various examples of valves being dithered, with various amplitudes.
• Figures 4-6 depict graphs in which controller boom-up valve 210 and controller boom-down valve 214 are both dithered, but the dithering of those valves is insufficient to cause dithering in their outputs.
• Figures 7-9 depict graphs in which controller boom-up valve 210, and controller boom-down valve 214 are both dithered, with a signal level greater than in figures 4-6, but their output pressure variations are present but insufficient to cause dithering in main valve 304.
• Figures 10-12 depict graphs in which controller boom-up valve 210 and controller boom-down valve 214 are dithered, with sufficient amplitude to produce dithered pressure control signals at main valve inputs 328 and 330.
• Figures 4-6 depict graphs of dithering electrical signals applied to controller boom-up valve 210, controller boom-down valve 214 by controller 202 and resulting hydraulic fluid pressures 602 applied to main valve 304 via 328 and 330.
• the graphs shown in Figures 4-6 have the same time scale and signal events are shown with respect to times To, T-i, T2, and T3, etc.
• Figure 6 shows that insufficient dither amplitude produces no dither in the outputs of either 210 or 214.
• FIG. 4 depicts graph 400 showing voltage over time of dithering electrical signal 402.
• dithering electrical signal 402 is a square wave that is added to controller boom-up valve 210 by controller 202.
• Dithering electrical signal 402 applied to controller boom-up valve 210 causes hydraulic fluid pressure to be output from controller boom-up valve 210 which is applied to main valve 304.
• Figure 5 depicts graph 500 showing voltage over time of signal 502.
• Signal 502 is applied to controller boom-down 214 by controller 202.
• Signals 402 and 502 are pulse width modulated signals having duty cycles selected to modulate hydraulic fluid pressure on the outputs of 210 and 214.
• signals 402 and 502 also have an additional signal that is changed depending on a desired hydraulic fluid pressure to be output from valves 210 and 214.
• dithering electrical signals 402 and 502 are 180 degrees out of phase. As shown in Figures 4 and 5, at time To, signal 402 is high and signal 502 is low. At time T 1 , signal 402 is low and signal 502 is high.
• the combination of the amplitude of signals 402 and 502 and being out of phase causes periodically varying hydraulic fluid pressure to be applied to inputs 328 and 330 of boom main valve 304. Since signals 402 and 502 are out of phase, the hydraulic fluid pressures applied to inputs 328 and 330 will also be out of phase.
• Main valve 304 applies hydraulic fluid pressure to hydraulic cylinder 110 in response to hydraulic fluid pressure at input 328 of main valve 304 from boom-up valve 210.
• Figure 6 depicts graph 600 of hydraulic fluid pressure over time at input 328 of main valve 304.
• Output pressure 602 is shown in Figure 6 having a constant value that, in one embodiment, can range from zero up to a value prior to hydraulic fluid pressure that will cause main valve 304 to actuate.
• controller boom-up valve 210 as shown in Figure 4, with minimal variation of hydraulic fluid pressure applied to input 328 of main valve 304 as shown by output pressure 602 in Figure 6, results in no movement in main valve 304 and no reduction in its stiction.
• Boom-down valve 214 can be operated in a manner similar to the operation of boom-up valve 210 as described above.
• Figures 7 and 8 depict graphs of hydraulic fluid pressures applied to inputs 328 and 330 of main valve 304 when boom-up valve 210 and boom-down valve 214 are dithered as shown, for example, in Figures 4 and 5 and no user inputs are being received.
• the graphs shown in Figures 7-9 have the same time scale and events are shown with respect to times To, Ti, T2, and T3, etc.
• Figure 7 depicts graph 700 showing hydraulic fluid pressure values at input 328 of main valve 304 over time.
• Flydraulic fluid pressure 702 is shown having values over time forming a sinusoidal shape that is the response of the valve to the dithering signal.
• Figure 8 depicts graph 800 showing hydraulic fluid pressure values at input 330 of main valve 304 over time.
• Hydraulic fluid pressure 802 is shown having values over time forming a sinusoidal shape that is in response to dithering boom-down valve 320.
• Figures 7 and 8 show that sinusoidal waveforms 702 and 802 are out of phase by 180 degrees.
• waveform 702 As shown in Figures 7 and 8, at time To hydraulic fluid pressure shown by waveform 702 is climbing higher while hydraulic fluid pressure shown by waveform 802 is descending lower. At time T 1 , waveform 702 is shown descending lower while waveform 802 is climbing higher. In one embodiment, this alternating high and low of waveforms 702 and 802 continues as long as user input commanding boom 102 to move is not received. The amplitudes of waveforms 702 and 802 shown in Figures 7 and 8 are insufficient to cause main valve 304 to dither.
• Figure 9 depicts graph 900 of hydraulic fluid pressure over time at output 332 and output 334 of main valve 304 in response to hydraulic fluid pressures applied to inputs 328 and 330 of main valve 304 as depicted in Figures 7 and 8, respectively.
• Hydraulic fluid pressure 902 at output 332 is shown in Figure 9 having a constant value that, in one embodiment, can range from zero up to a value prior to hydraulic fluid pressure that would cause hydraulic cylinder 110 to move.
• Hydraulic fluid pressure 904 at output 334 is shown in Figure 9 having a constant value that, in one embodiment, can range from zero up to a value prior to hydraulic fluid pressure that would cause hydraulic cylinder 110 to move.
• Figures 10 and 11 depict graphs of hydraulic fluid pressures applied to inputs 328 and 330 of main valve 304 when no user inputs are being received.
• the graphs show increased dither amplitude, and also show that sinusoidal waveforms 1002 and 1102 are still out of phase by 180 degrees
• the graphs shown in Figures 10-12 have the same time scale and events are shown with respect to times To, Ti, T2, and T3, etc.
• Figure 10 depicts graph 1000 showing hydraulic fluid pressure values at input 328 of main valve 304 over time. Flydraulic fluid pressure 1002 is shown having values over time forming a sinusoidal shape that is in response to dithering of boom-up valve 210.
• Figure 11 depicts graph 1100 showing hydraulic fluid pressure values at input 330 of main valve 304 over time. Hydraulic fluid pressure 1102 is shown having values over time forming a sinusoidal shape that is in response to dithering boom-down valve 214.
• waveforms 1002 and 1102 are similar to waveforms 700 and 800. Each of waveforms 702, 802, 1002, and 1102 depicts periodically varying hydraulic fluid pressure at a particular point. The amplitudes of waveforms 1002 and 1102 are higher than the amplitudes of waveforms 702 and 802. The higher amplitudes of waveforms 1002 and 1102 cause main valve 304 to dither which mitigates stiction of main valve 304.
• Figure 12 depicts graph 1200 showing hydraulic fluid pressure applied to input 328 and hydraulic fluid pressure applied to input 330 over time.
• waveform 1202 is out of phase with waveform 1204 by 180 degrees.
• the alternating pressures applied via inputs 328 and 330 are in response to dithering valve 210 and 214 with an amount of dither that exceeds the amount necessary just to reduce their stiction.
• the dithering of main valve 304 overcomes the stiction of main valve 304.
• the hydraulic fluid pressure applied to inputs 328 and 330 do not contain enough sinusoidal variations cause variations in the outputs 332 and 334, and therefore hydraulic cylinder 110 does not move in response to the dither.
• the stiction of main valve 304 is mitigated without causing movement of hydraulic cylinder 110.
• the graph of signal 1002 in Figure 10 can be modified with the addition of a control signal, such that the shape remains the same but the average pressure level is higher, causing main valve 304 to shift and create pressure at 332, extending cylinder 110 and raising boom 102.
• the graph of signal 1102 in Figure 11 can be modified with the addition of a control signal, such that the shape remains the same but the average pressure level is higher, causing main valve 304 to shift and create pressure at 334, retracting cylinder 110 and lowering boom 102.
• the net amount of dither to main valve 304 can be adjusted by varying the amplitudes dither signals 402 and 502. This net amount can also vary based on the value of the control signal added in graph 1000 or 1100, such that the net difference to main value 304 remains the same but the inactive opposite side reaches zero and it corresponding dither disappears, replaced by dither only on the active side. This remaining active dither + control signal would be equal to the amount needed to both control output 332 or 334, and reduce stiction in main valve and the corresponding active controller valve.
• FIG. 13 depicts a flowchart of a method 1300 for mitigating stiction of valves (i.e., two pilot control valves and a main valve) of a hydraulic system according to an embodiment.
• a first hydraulic valve is dithered, with a signal beyond what is needed to remove its inherent dither.
• boom-up control valve 210 shown in Figure 3 is dithered.
• a second hydraulic valve 214 is dithered, also with a signal beyond what is needed to remove its inherent dither.
• the dithering of boom- up valve 210 and boom-down valve 214 causes hydraulic fluid pressure to be applied to inputs 328 and 330 of main valve 304 as shown in Figures 10 and 11 .
• main valve 304 is dithered by the hydraulic fluid pressure applied to inputs 328 and 330. Dithering of main valve 304 reduces or eliminates stiction in spool 12 of the main valve 304. In one embodiment, the variations in pressures at 328 and 330 are sufficient to mitigate stiction of spool 12 in main valve 304, but are insufficient to cause hydraulic fluid pressure variations in outputs 332 and 334 and to cause hydraulic cylinder 110 to move in response.
• an input to actuate hydraulic cylinder 110 is received by controller 202 shown in Figure 2.
• input is received from a joystick of input 208 shown in Figure 2.
• controller 202 outputs a signal to one of controller boom- up 210 or controller boom-down 214 shown in Figure 3 in response to the joystick input.
• the signal causes hydraulic fluid pressure to be added to the dither signal and applied by valve 210 to input 328 or valve 214 to input 330 of main valve 304.
• Valve 304 responds to the net difference in pressure at inputs 328 and 330, and, at step 1312, the hydraulic cylinder 110 is actuated by the hydraulic fluid pressure applied via outputs 332 or 334 of main valve 304.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Mechanical Engineering (AREA)
• Mining & Mineral Resources (AREA)
• Civil Engineering (AREA)
• Structural Engineering (AREA)
• Chemical & Material Sciences (AREA)
• Analytical Chemistry (AREA)
• Operation Control Of Excavators (AREA)
• Fluid-Driven Valves (AREA)

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• 2019
  • 2019-09-27 US US16/585,784 patent/US11408449B2/en active Active
• 2020
  • 2020-08-22 WO PCT/US2020/047544 patent/WO2021061316A1/en active Application Filing
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  • 2020-08-22 EP EP20781131.6A patent/EP4034772A1/en active Pending
  • 2020-08-22 CN CN202080052565.8A patent/CN114144589B/zh active Active

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